Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
  • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
  • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
  • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
  • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
  • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
  • F16D55/28—Brakes with only one rotating disc
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
  • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/02—Braking members; Mounting thereof
  • F16D2065/13—Parts or details of discs or drums
  • F16D2065/1304—Structure
  • F16D2065/1312—Structure circumferentially segmented
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D65/00—Parts or details
  • F16D65/02—Braking members; Mounting thereof
  • F16D2065/13—Parts or details of discs or drums
  • F16D2065/134—Connection
  • F16D2065/1372—Connection outer circumference
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D2121/00—Type of actuator operation force
  • F16D2121/18—Electric or magnetic
  • F16D2121/20—Electric or magnetic using electromagnets
  • F16D2121/22—Electric or magnetic using electromagnets for releasing a normally applied brake

Definitions

• an electro-magnetically released friction safety brake with two brake disks and an axially displaceable, non-rotatable electromagnet is shown.
• the two brake discs are axially displaceable on a rotating central hub on both sides of the electromagnet and are clamped during braking by compression springs in the coil carrier between the armature disc and a flange plate on the one hand and the coil carrier housing and a machine wall on the other.
• the rotating parts are located inside the brake, which does not have to be useful in every conceivable installation situation.
• a rotatable part of a brake of the same type which can be referred to as a hub, is designed such that it envelops all the other components of the brake or radially outward encloses, i.e. the rotating brake discs, the coil carrier with the compression springs and the armature disc acted upon by it.
• This construction has the disadvantage, among other things, that the connection between the rotating hub and the brake discs takes place via a complex and space-consuming internal or external toothing of the hub and brake discs.
• This prior art is a dual-circuit brake, each with a friction element, on the left and right of the centrally arranged coil carrier with the armature disk. In addition, the coil carrier with armature disk is floating.
• DE-OS 197 33 169 shows only the features of the preamble of claim 1.
• Part 3 is a fixed machine wall (column 10, line 24) and part 67 an arcuate spring blade (column 10, lines 59 ff). They appear to have a relationship to the friction lining carrier (7) according to the present invention only as a result of their representation in FIG. 7, which, however, turns out to be a misinterpretation on closer inspection.
• DE-OS 41 05 358 shows a motor vehicle brake with a cup-shaped part 14 of a brake housing 13, brake disks 16 and an electromagnetic application device 18, that is to say features which are already assumed to be known.
• DE-PS 35 39 805 describes an electromagnetically actuated spring pressure brake with the usual features.
• a leaf spring 10 is shown in FIGS. 3 and 4, but there is no similarity with the spring of the brake according to the invention.
• DE-OS 36 20 797 represents an electromagnetic brake with radially acting brake shoes and is not comparable with the present invention.
• DE-OS 14 00 084 an electromagnetic multi-plate clutch is shown.
• part 3 is a brake caliper encompassing the inside.
• the vehicle brake according to US-PS 24 65 394 is designed for this special purpose.
• it is also known to design brakes of the type assumed here, inter alia, as dual-circuit brakes by dividing the armature disk and its electromagnetic action radially or diagonally.
• FIG. 1 shows a vertical section through the essential parts of the electromagnetic brake according to the invention, which is integrated in a rotating traction sheave 1;
• FIG. 2 shows the lower half (below the center line of FIG. 1) of a similar section in a somewhat different embodiment of the braking parts of this arrangement;
• 3 shows a top view of FIG. 1 from the left with the traction sheave 1 removed to better illustrate the four lamellae 9, for example, which connect the traction sheave 1 to the friction lining carrier 7;
• FIG. 4 shows a section similar to FIG. 1, but with a diagonally divided magnetic coil or armature disk to form a so-called dual-circuit brake;
• FIG. 5 shows a sectional view in a basic representation perpendicular to the rotational axis of the brake to illustrate the embodiment according to FIG. 4;
• FIGS. 4-5 shows a similar representation of a brake according to the invention as a dual-circuit brake similar to FIGS. 4-5, but with a concentrically divided magnet coil and armature disk, but otherwise the same functional principles;
• FIG. 8a / b two details from FIG. 6 (see the circle at the top right) in a view axially from the front (FIG. 8a) and radially from the outside (FIG. 8b);
• Fig. 9-10 a Fig. 4/5 or 6/7 similar representation of a slightly different embodiment of a brake according to the invention as a dual-circuit brake with a concentric division of the solenoid and armature disk, the friction lining 7 from radially inside into the gap between the armature and engine / transmission 5 engages.
• a traction sheave 1 which is essentially cup-shaped and has a central hub, is rotatably mounted on a motor or transmission or the like (reference number 5), also not shown, in a manner not shown.
• the cup-shaped traction sheave can actuate an elevator, for example, via ropes guided over it, or serve for other drive purposes via belts or the like.
• a special characteristic of this electromagnetic brake is the accommodation of the annular coil carrier 2 with the magnetic coil 12 embedded therein in the annular interior of the traction sheave 1, together with the armature disc 6 which is axially displaceable under the influence of the springs 11 or the magnetic coil 12 annular friction lining carrier 7 with the friction linings 8 arranged on its two end faces radially from the outside into the gap between the stationary motor / transmission (reference number 5) and the armature disk 6, which is also still arranged within the rotating traction sheave 1.
• the friction lining carrier extends radially inward from the radially outer edge of that end face of the traction sheave (cup-shaped in its outer region) which faces the motor / transmission 5. In this way, a particularly compact and space-saving design is achieved and, at the same time, the parts causing the actual braking are shielded particularly well from the surroundings.
• the annular coil carrier 2 with the magnet coil 12 embedded therein is fastened to the motor (or gearbox or mounting bracket) 5 via a plurality of cylinder head screws 3 distributed over the circumference.
• the armature disk 6 is non-rotatably but axially movably connected to the coil carrier 2, ie it is guided in the axial direction by the intermediate sleeves 4 of the screws 3.
• four lamellae 9 in the form of circular ring segments are each connected to the aforementioned end face of the traction sheave 1 via a screw 13 arranged in the center thereof, as is shown in FIG. 3 and in FIG can be seen.
• Each of these lamellae 9 is also connected to the friction lining carrier 7 by two screws 10, each at the end of the lamellae, as shown in FIG. 3 and in FIG. 1 on the upper front edge of the drive pulley.
• Two friction linings 8 are attached to this friction lining carrier 7.
• the friction lining carrier 7 is therefore provided with four fins 9 on the lateral edge on the axially inner end face of the driving disc attached, in the vicinity of the circumference or on the front edge of the peripheral flange of the traction sheave.
• the armature disk 6 in FIG. 1 is tightened to the left against the force of the compression spring 11 and the friction lining carrier 7 provided with the two friction linings 8, which in the normal operating state is resiliently coupled to the drive disk 1 via the lamellae 9 , can circulate freely. If the current is removed from the solenoid 12, the armature disk 6 is pressed towards the motor (or gearbox or mounting bracket) 5 by the pressure of the springs 11 distributed on the circumference, with the result that the two friction linings 8 are in frictional engagement with the come in each case opposite end face and braking is thus initiated.
• FIG. 2 shows an alternative to the design of FIG. 1 in more detail.
• This is an embodiment with two annular friction lining carriers 7 arranged parallel to one another, each with two friction linings, that is to say one friction lining on each side.
• the friction lining carriers 7 are connected via a plurality of pins 15 distributed over the circumference (similar to the fastening screws 13 from FIG. 1) to the one end face of the radially outermost part of the traction sheave 1 with which these friction lining carriers 7 rotate.
• the intermediate disk 14 is connected to the armature disk 6 in a rotationally fixed but axially displaceable manner via a plurality of pins 16 distributed over the circumference. is axially movable but immobile in the circumferential direction.
• the configuration of the alternative embodiment in FIG. 2 significantly increases the available friction surface and thus the friction torque that can be achieved by the brake.
• FIGS. 4 and 5 Such an embodiment of the brake according to the invention is shown in FIGS. 4 and 5: Both the magnetic coil 12 and the annular armature disk 6 are divided diagonally into two identical parts which are independent of one another, as can be seen particularly clearly from FIG. 5.
• FIGS. 6-8 Another such embodiment of a two-circuit brake is shown in more detail in FIGS. 6-8, in which the armature disk 6 and the magnet coil 12 are divided concentrically into two mutually independent parts. A detail of FIG.
• FIG. 8 a view from the front axially (top view) and a view from the outside radially (show below).
• FIGS. 4 and 5 or 6-8 are basically of the same design with respect to the present invention, ie with a friction lining carrier 7 connected to the front edge of the traction sheave and radially engaging from the outside in the gap between the armature disk 6 and the machine element 5
• the components of the further designs of FIGS. 4-8 corresponding to the first embodiment have the same reference numerals and are not described again here.
• the armature disk and the magnetic coil are each made twice or independently of one another, namely diagonally divided on the one hand and concentric on the other.
• the spring pressure ie Compression springs 11
• each armature disk part to be carried out twice; this is only hinted at in the drawings - of course, several such compression springs are uniformly distributed on the circumference of the brake.
• Figures 8a and 8b show the detail X of Figure 6 (the dash-dotted circle at the top right), d. H. an alternative to the other embodiments of connecting the rotating traction sheave 1 to the friction lining carrier 7 of FIG. 6:
• eight axially projecting claws 17 are provided on the circumference of the traction sheave 1, one claw 17 of which is shown in FIGS. 8a and 8b , each with the direction of view as indicated in Figure 6 by the two arrows.
• the axially projecting claw 17 engaging in a correspondingly shaped or milled circumferential recess in the traction sheave 1, the drive connection between the traction sheave 1 and the friction lining carrier is established.
• a suitable U-shaped plastic part 18 is pressed into the milled circumferential recess in the drive pulley 1.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Electromagnetism (AREA)
• Braking Arrangements (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=7630690

Family Applications (1)

Country Status (7)

Cited By (4)

Families Citing this family (7)

Citations (4)

Family Cites Families (8)

• 2000
  • 2000-02-11 DE DE10006255A patent/DE10006255A1/de not_active Withdrawn
• 2001
  • 2001-02-09 DE DE50106032T patent/DE50106032D1/de not_active Expired - Lifetime
  • 2001-02-09 EP EP01915211A patent/EP1254323B1/de not_active Expired - Lifetime
  • 2001-02-09 ES ES01915211T patent/ES2238428T3/es not_active Expired - Lifetime
  • 2001-02-09 WO PCT/EP2001/001410 patent/WO2001059317A1/de active IP Right Grant
  • 2001-02-09 CN CNB018048234A patent/CN1283934C/zh not_active Expired - Fee Related
  • 2001-02-09 KR KR1020027010271A patent/KR20020084119A/ko not_active Application Discontinuation
  • 2001-02-09 JP JP2001558626A patent/JP2003525400A/ja not_active Withdrawn

Patent Citations (4)

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